CN107429805A - The torque cam mechanism device of automatic transmission - Google Patents

The torque cam mechanism device of automatic transmission Download PDF

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Publication number
CN107429805A
CN107429805A CN201680017852.9A CN201680017852A CN107429805A CN 107429805 A CN107429805 A CN 107429805A CN 201680017852 A CN201680017852 A CN 201680017852A CN 107429805 A CN107429805 A CN 107429805A
Authority
CN
China
Prior art keywords
driving cam
cam
face
driving
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201680017852.9A
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Chinese (zh)
Inventor
横山和彦
福井秀行
田中雅人
横手达男
土屋郎
土屋一郎
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JATCO Ltd
Original Assignee
JATCO Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JATCO Ltd filed Critical JATCO Ltd
Publication of CN107429805A publication Critical patent/CN107429805A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/186—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions with reciprocation along the axis of oscillation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F16H55/566—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable only adjustable when pulley is stationary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/26—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members with members having orbital motion

Abstract

A kind of torque cam mechanism device of automatic transmission, it possesses：Driving cam part (91,92), it has the driving cam face (91D, 92C) of ring-type, receives rotation torque and rotated；By driving cam part (92, 93), it has and driving cam face (91D, 92C) relative ring-type by driving cam face (92D, 93C), via ball (95) and pass through driving cam part (91, 92) it is driven in rotation, driving cam face and by driving cam face by all-round at least two deciles of ring-type, and there is helical form curved surface corresponding with cam angle degree respectively, halved helical form curved surface it is mutual formed with connecting portion (91J, 92J, 93J), in driving cam face, by at least one party in the helical form curved surface in driving cam face, the guide groove (92G) of guiding ball movement is continuously provided with throughout complete cycle.

Description

The torque cam mechanism device of automatic transmission
Technical field
The present invention relates to the torque cam mechanism device of automatic transmission.
Background technology
Disclose a kind of skill of the thrust generation mechanism using cam mechanism as the gear of variable v-belt drive Art (for example, referring to patent document 1,2).
This cam mechanism is the mechanism that thrust is produced according to the rotational phase difference of two cam parts, in each cam part It is upper to be formed respectively relative to the ring-type with rotating shaft direct cross towards axially inclined cam surface, pass through the mutual folder in cam surface Ball (rotor) is filled, produces rotational phase difference on two cam parts, thus each cam surface mutually slides via ball, together When, two cam parts carry out clutch, and its total length (axially long) changes and produced to the power (thrust) for rotating direction of principal axis.
On two cam parts, multigroup relative cam surface is provided with defined radial position, is pacified between each cam surface Equipped with one or more balls.If consider thrust-balancing, two groups of cam surface subsistence level, in addition, by each cam surface Multiple balls are clamped each other, can mitigate the load of each ball or each cam surface.
For example, Figure 16 (a) is the stereogram for the side for representing the cam part 101 disclosed in patent document 2, in cam part Part 101 is provided with 4 cam surfaces 102 circumferentially helically extended.Ball is equipped with these each cam surfaces 102 103.Ball 103 along the arrow mark shown in Figure 16 (a) and in the range of the circumferential stroke of the arrow mark relative to Cam surface 102 relatively moves, meanwhile, contribute to smoothly rotating against between cam part and thrust to produce.
But in above-mentioned cam mechanism, there is following problem.
That is, on each cam surface 102, ball 103 relatively moves (rotation) along cam surface 102, meanwhile, contribute to thrust Produce, limited shown in the movement of ball 103 such as Figure 16 (b) near the end of cam surface 102.On each cam surface 102 During equipped with multiple balls 103, if setting a diameter of d of the ball 103b, cam surface 102 circumferential total length be LC1, then multiple (n It is individual) the removable stroke L of ball 103BSSuch as following formula, if the quantity of increase ball, the removable stroke L of ball 103BSReduce.
LBS=LC1- n × db
Because by the removable stroke L of ball 103BSThe amount of relative rotation of two cam parts is limited, so in order to true Protect the axially opposite amount of movement of two cam parts, it is necessary to reduce the quantity or the spiral helicine cam surface 102 of increase of ball 103 The radius of spin or the spiral helicine cam surface 102 of increase angle of inclination (relative to the periphery orthogonal with central axis CL Angle of inclination) α.
If reducing the quantity of ball 103, it is difficult to produce the high thrust that the load of each ball or each cam surface increases, If increasing the radius of spin of cam surface 102, the maximization of device can be caused, if increase tilt angle alpha, for high thrust Speech, it is impossible to swimmingly carry out rotating against for two cam parts, it is difficult to produce high thrust.
Accordingly, it is difficult to ensure the axially opposite amount of movement of two cam parts, applied to variable v-belt drive can During movable belt pulley, there is the axial movement stroke that can not substantially ensure that movable pulley, and then, it is impossible to substantially ensure that automatic transmission This problem of gear range.
Patent document 1：(Japan) opens clear 58-38055 publications in fact
Patent document 2：(Japan) JP 60-26844 publications
The content of the invention
The present invention be in view of the problem and set up, its object is to provide a kind of automatic transmission torque cam mechanism dress Put, it can clamp multiple balls between cam surface, and not increase the angle of inclination of cam surface, it can be ensured that the length of each cam surface, High thrust can be produced, and can fully ensure the gear range of automatic transmission.
(1) to achieve these goals, the torque cam mechanism device of automatic transmission of the invention, it will be in automatic transmission The rotation torque of interior transmission is converted to axial thrust, wherein, possess：Driving cam part, it has the first driving of ring-type Cam surface, receive rotation torque and rotated；By driving cam part, it has relative with the first driving cam face The first of ring-type is via ball and convex by the driving cam part rotation driving, first driving by driving cam face Wheel face and described first by driving cam face by all-round at least two deciles of ring-type, and there is spiral shell corresponding with cam angle degree respectively Revolve shape curved surface, halved helical form curved surface it is mutual formed with connecting portion, in the first driving cam face and described the One at least on a helical form curved surface, guiding institute is continuously provided with throughout complete cycle in the helical form curved surface in driving cam face State the guide groove of the movement of ball.
(2) preferably, the connecting portion possesses：First link surface, it is from two connected each other by the connecting portion The end of the helical form curved surface of side in helical form curved surface axially extends；Second link surface, it links described first and linked The end of the helical form curved surface of the end in face and the opposite side in the two helical forms curved surface, second link surface are set to relative In the vertical face of axis direction.
(3) preferably, the guide groove possesses：Helical form groove portion, it is formed as along the helical form curved surface Helical form；Connection groove section, it forms in the mutual of the helical form groove portion, the helical form groove portion is smoothly connected.
(4) preferably, in the inside of the guide groove, multiple balls are equipped with series connection.
(A) preferably, the guide groove, which possesses, makes a part for the ball can be from helical form curved surface protrusion Opening portion, the more than half part of the ball is stored, and the opening wide cut of the opening portion is smaller than the external diameter of the ball.
(B) preferably, the opening portion of the guide groove a part formed with order to the ball is inserted The inside of the guide groove and expanding insertion wide diameter portion, in the insertion wide diameter portion formed with described in preventing after insertion The anti-delinking part that ball departs from from the inside of the guide groove.
(C) preferably, the insertion wide diameter portion with phase angle to correspondingly the axially projecting helical form On curved surface, it is formed to the position of less than half that the overhang of axial direction is whole overhangs.
(D) preferably, the anti-delinking part by by by the insertion with wide diameter portion it is expanding it is partially enclosed in a manner of install Screwed part formed.
(5) preferably, intermediate cam component is also equipped with, it with the first driving cam face at one end formed with can connect Tactile second is by driving cam face, in the other end formed with can be with the described first the second driving cam contacted by driving cam face Face, relative to the driving cam part and it is described can be rotated against by driving cam part, from the driving cam part To it is described by driving cam part enter action edge transmit when, the first driving cam face and described second is supported by driving cam face Connect, from it is described by driving cam part to the driving cam part enter action edge transmit when, described first by driving cam Face and the second driving cam face abut, and realize power transmission.
(E) preferably, the first driving cam face, described first by driving cam face, described second by drive it is convex Wheel face and the second driving cam face are respectively provided with the helical form curved surface, in being formed respectively each other for the helical form curved surface Have the connecting portion, from the driving cam part to it is described by driving cam part enter action edge transmit when, described first Abutted by the connecting portion in driving cam face and the connecting portion in the second driving cam face, from it is described driven it is convex When wheel component enters action edge to the driving cam part and transmitted, the connecting portion in the first driving cam face and described the Two are abutted by the connecting portion in driving cam face.
(F) preferably, described each second by driving cam face and its mutual joint face and described each the Two driving cam faces and its mutual foregoing joint face mutually stagger phase and configured.
(G) preferably, the first driving cam face and described first by driving cam face or it is described first driving it is convex It is wheel face, described first all identical by driving cam face and the second driving cam face by driving cam face, described second Cam angle degree.
(H) this automatic transmission be possess including be made up of fixed pulley and movable pulley two pulley arrangements, winding In the automatic transmission of the stepless speed changing mechanism for the band for entering action edge transmission in described two pulley arrangements, wherein, possessing makes Either one of described two pulley arrangements produces the above-mentioned torque cam mechanism device of clamping force.
(I) preferably, the torque cam mechanism device makes the driving cam part be rotated integrally with the movable pulley, Make described to be rotated integrally by driving cam part and the fixed pulley.
(J) preferably, the intermediate cam component can be pacified with the relative rotation relative to the rotary shaft of the pulley arrangement Dress.
According to the present invention, ball is set to be moved on complete cycle in continuous guide groove, so can be installed between cam surface multiple Ball, and do not increase the angle of inclination of cam surface, it can be ensured that the length of each cam surface.Thus, for example become for belt continuous variable In the case of the thrust generation mechanism of the gear of fast device, it is not necessary to which aggrandizement apparatus can just produce big thrust and can be abundant Ensure gear range.
Brief description of the drawings
Fig. 1 is the structure of the major part of the drivetrain unit of the vehicle for the automatic transmission for possessing an embodiment of the present invention Cheng Tu；
Fig. 2 is the axle of the major part of the drivetrain unit of the vehicle for the automatic transmission for possessing an embodiment of the present invention Configuration diagram；
Fig. 3 is the power transmission of the drivetrain unit of the vehicle for the automatic transmission that explanation possesses an embodiment of the present invention The figure of pattern, (a) are CVT low modes, and (b) is CVT high range modes, and (c) is direct-connected pattern；
Fig. 4 is the figure of one of the speed change image for the automatic transmission for representing an embodiment of the present invention；
Fig. 5 is the schematical pie graph for the torque cam mechanism device for illustrating an embodiment；
Fig. 6 is the stereogram of the cam part of the torque cam mechanism device of an embodiment of the present invention, and (a) represents intermediate cam Part, (b) represent driving cam part and by driving cam parts；
Fig. 7 is the schematical side face view of the manner of execution for the torque cam mechanism device for illustrating an embodiment of the present invention, (a) represent to make the consistent state of the phase of each cam part, (b) represents the state for shifting to an earlier date the phase of driving cam part, (c) Represent the state for making the phase delay of driving cam part；
Fig. 8 is the schematical side face view of the effect for the torque cam mechanism device for illustrating an embodiment of the present invention, (a)~ (c) process that the driving cam part of this torque cam mechanism device shifts to an earlier date phase is represented successively, and (d) represents comparative example；
Fig. 9 is the schematical side face view of the effect for the torque cam mechanism device for illustrating an embodiment of the present invention, (a) table Show the cam part of comparative example, (b) represents the cam part of this torque cam mechanism device；
Figure 10 is the figure of the detailed configuration of the cam part for the torque cam mechanism device for representing an embodiment of the present invention, (a) It is its stereogram, (b) is the expanded view of its outer peripheral face, and (c) is the expanded view in the section of the core of its guide groove；
Figure 11 is the figure of the cam part for the torque cam mechanism device for representing an embodiment of the present invention, and (a) is its front elevation (Figure 10 (a) A direction views), (b) are its front elevations (Figure 10 (a) B direction views), and (c) is its main portion sectional view (Figure 11 (a) C-C regarding sectional views), (d) is its main portion sectional view (Figure 11 (a) D-D regarding sectional views)；
Figure 12 is the enlarged view of the main part of the cam part of the torque cam mechanism device of an embodiment of the present invention, and (a) is To regarding enlarged drawing, (b) is Figure 10 (b), (c) I to regarding enlarged drawing by Figure 10 (b), the H of (c)；
Figure 13 is the enlarged view of the main part of the cam part of the torque cam mechanism device of an embodiment of the present invention, and (a) is Figure 11 (d) G portions enlarged drawing, (b) are Figure 11 (b) E portions enlarged drawings, and (c) is Figure 11 (b) F-F amplification regarding sectional views；
Figure 14 is matching somebody with somebody for the insertion wide diameter portion of the cam part for the torque cam mechanism device for illustrating an embodiment of the present invention The figure put, (a) are the inclined expanded views for representing its guide groove, and (b) is the front elevation of its guide groove；
Figure 15 is the stereogram of the cam part of the torque cam mechanism device of the variation of an embodiment of the present invention, (a) table Show and driving cam part is represented by driving cam part, (b)；
Figure 16 is the figure of the torque cam mechanism device for the background technology for representing the problem of the present invention, and (a) is that its major part is stood Body figure, (b) are the figures for the removable stroke for representing the ball in its cam surface.
Embodiment
Hereinafter, with reference to the accompanying drawings of the embodiment of the automatic transmission used for electric vehicle of the present invention.It is in addition, as shown below Embodiment strictly speaking only illustrate, not by the various modifications do not expressed in following embodiment or technology Using the intention of exclusion.It can be implemented in part with the embodiment, either change a part and implemented or replaced Implemented for other mechanisms or device with equal function.
The electric automobile (hereinafter also referred to as vehicle) of present embodiment is only to be travelled motor as driving source Electric automobile (also referred to as EV), do not include selectively moving motor and internal combustion engine as the mixing that driving source is travelled Power automobile.In addition, this automatic transmission is arranged between the motor and driving wheel of this vehicle.
(composition of drivetrain unit)
First, the drivetrain unit of vehicle is illustrated.As shown in Figures 1 and 2, the drivetrain unit possesses：As vehicle The main motor (also referred to as motor) 1 of driving source, the speed changer that there is the output shaft with main motor 1 integrally to link input Axle (hereinafter referred to as input shaft) 2A automatic transmission 2, the reducing gear 6 being connected with automatic transmission 2, connect with reducing gear 6 The differential attachment 7 connect.It is not shown respectively in connection with having on axletree 7L, 7R that the axle shaft gear of the left and right with differential attachment 7 is connected Driving wheel.
Automatic transmission 2 is to be attached with direct-connected tooth in the variable v-belt drive (CVT) of so-called band pair gear Take turns the speed changer of mechanism 20.Automatic transmission 2 possesses：Band 37 with power transmission, can be with the relative rotation with input shaft 2A It is configured with primary pulley (input unit) 30P band type stepless speed changing mechanism (hereinafter also referred to gear) 3 and the gear The always engagement type parallel-axis type gear shift that 3 secondary pulley (output section) 30S rotary shaft 36 links is (following to be also referred to as For secondary gear) 4, it is in a manner of around gear 3 and secondary gear 4 that input shaft 2A and reducing gear 6 is direct-connected Direct-connected gear mechanism 20.
Gear 3 possesses：The primary pulley being made up of the fixed pulley 31 with rotary shaft 33 and movable pulley 32 30P, the secondary pulley 30S being made up of the fixed pulley 34 with rotary shaft (output shaft) 36 and movable pulley 35, it is wound in just Band 37 on level belt wheel 30P and secondary pulley 30S V-groove.The rotary shaft 33 of primary pulley 30P fixed pulley 31 is configured to It can be rotated against with input shaft 2A.
In addition, in Fig. 1 respectively using gear ratio as low-grade side state and high-grade side state representation gear 3 just Level belt wheel (pulley arrangement) 30P, secondary pulley (pulley arrangement) 30S and band 37.Primary pulley 30P, secondary pulley 30S it is each The half portion in outside (separated side) represents the state of low-grade side, and the half portion in each inner side (side close to each other) represents The state of high-grade side.For band 37, the state of low-grade side is schematically shown with solid line, is used in each belt wheel 30P, 30S inner side Double dot dash line schematically shows the state of high-grade side.But the high-grade state represented with double dot dash line only represents belt wheel and band Radial direction position relationship, it is actual can not be in the inner side half portion performance of belt wheel with position.
The gear ratio that the change of the primary pulley 30P and secondary pulley 30S of the gear 3 tape wrapping radius is realized Adjustment and belt wheel axle thrust (also referred to as thrust) i.e. adjustment with clamping force are by electric actuator 80A and mechanical counter-force mechanism To perform.As mechanical counter-force mechanism, using there is torque cam mechanism mechanism.The torque cam mechanism mechanism has spiral by end respectively The cam part of a pair of ring-types of the inclined cam surface of shape is formed, and is configured in a manner of each cam surface is mutually sliding on coaxial, In addition, rotating against according to a pair of cams part, a pair of cams part is in axially mutual clutch, by changing a pair of cams portion The total length of part, adjustment are crimped on the thrust of the rotary part (belt wheel 30P, 30S) on a cam part.
Here, primary pulley 30P and secondary pulley 30S use torque cam mechanism mechanism as mechanical counter-force mechanism.By This, the reaction force of primary pulley 30P and secondary pulley 30S power (power for separating belt wheel), two belt wheels are pressed as band 37 Each ball-type torque cam mechanism mechanism play a role, it is not necessary to using oil pressure etc. but two belt wheel 30P, 30S is produced with band 37 Transmit thrust corresponding to moment of torsion.
In addition, the electric actuator of a side of active ground rotation driving a pair of cams part is equipped with primary pulley 30P 80A, to change the total length of a pair of cams part, the groove width of adjustment primary pulley 30P V-groove.In addition, in present embodiment In, as each torque cam mechanism mechanism, using the ball moment of torsion that the slide connecting part of each cam surface is divided into the point contact via ball Cam mechanism.
So, it is that a pair of torque cam mechanism mechanism and rotation driving are convex by mechanical counter-force mechanism on primary pulley 30P The electric actuator 80A of one side of wheel component changes the total length of a pair of cams part, adjustment primary pulley 30P V-groove Groove width and adjust gear ratio, and adjust belt wheel 30P thrust and adjust band clamping force.Therefore, by by primary pulley 30P electricity The mechanism that acting actuator 80A and torque cam mechanism mechanism are formed is also referred to as gear 8.On the other hand, secondary pulley 30S moment of torsion Thus cam mechanism produces secondary pulley 30S thrust, therefore also referred to as thrust generation mechanism 9.On these gears 8 And thrust generation mechanism 9, its aftermentioned details.
Secondary gear 4 has multiple speed change levels (being herein high-grade, low-grade two-stage), and possess to be provided to the relative rotation With the secondary pulley 30S of gear 3 rotary shaft 36 it is coaxial one rotary shaft 43 on gear 41,42, with rotary shaft The gear 44,45 that the mode that 43 parallel rotary shafts 46 rotate integrally is fixedly installed.Gear 41 and gear 44 always engage, and form 2 fast (top grade) gears.Gear 42 and gear 45 always engage, and form 1 fast (low grade) gear.
In order to selectively switch 2 fast gears and 1 fast gear, the nibbling equipped with three-position type on secondary gear 4 Close clutch mechanism 5B.Meshing clutch mechanism 5B possesses：The clutch hub 54 that is rotated integrally with rotary shaft 43, have with setting In clutch hub 54 external tooth 54a splines engage internal tooth 55a sleeve 55, make sleeve 55 to shifting direction (axial direction) move Selector fork 56, drive selector fork 56 switching electric actuator 50B.
The external tooth 41a engaged with the internal tooth 55a of sleeve 55 is provided with gear 41, is provided with and sleeve 55 on gear 42 The external tooth 42a of internal tooth 55a engagements.
Sleeve 55 has fast (low grade) gear of the 2 fast positions (H) of fast (top grade) gear of neutral position (N), setting 2, setting 1 1 each gear of fast position (L), driving is slided between each gear by selector fork 56.
If driving selector fork 56 by electric actuator 50B, make sleeve 55 mobile to the side of gear 41 (that is, 2 fast position), Then the internal tooth 55a of sleeve 55 engages with the external tooth 41a of gear 41, and rotary shaft 43 and gear 41 rotate integrally, and sets 2 fast speed changes Shelves.If setting 2 fast gears, from the secondary pulley 30S of gear 3 rotary shaft 36 (that is, rotary shaft 43) via tooth Wheel 41, gear 44, rotary shaft 46 enter action edge transmission to reducing gear 6.
If driving selector fork 56 by electric actuator 50B, make sleeve 55 mobile to the side of gear 42 (that is, 1 fast position), then The internal tooth 55a of sleeve 55 engages with the external tooth 42a of gear 42, and rotary shaft 43 and gear 42 rotate integrally, and sets 1 fast gear. If setting 1 fast gear, from the secondary pulley 30S of gear 3 rotary shaft 36 (that is, rotary shaft 43) via gear 42nd, gear 45, rotary shaft 46 enter action edge transmission to reducing gear 6.
In addition, in order that the internal tooth 55a of sleeve 55 smoothly nibbles with the external tooth 41a of gear 41 or the external tooth 42a of gear 42 Close, carry out rotation Synchronization Control described later, so and need not need not be equipped with lazy-tongs in site of engagement.
Direct-connected gear mechanism 20 possesses the input gear (input gear) 21 that can be configured with the relative rotation with input shaft 2A, As shown in Fig. 2 one of multiple change-speed gearings of the input gear 21 and secondary gear (here, the output for 1 fast gear Side gear is gear 45) engage and linked by driving.
In addition, above-mentioned input gear 21 and gear 45 are set as that the respective number of teeth is substantially the same, gear ratio is substantially set to 1.0。
In order to selectively use direct-connected gear mechanism 20 and gear 3, equipped with the engagement clutch machine of three-position type Structure 5A.Meshing clutch mechanism 5A is formed in the same manner as meshing clutch mechanism 5B as illustrated in fig. 1, is possessed and input shaft 2A mono- The clutch hub 51 of body rotation, the sleeve with the internal tooth 52a engaged with located at the external tooth 51a splines of clutch hub 51 52nd, sleeve 52 is made to the mobile selector fork 53 of shifting direction (axial direction), the switching electric actuator of driving selector fork 53 50A。
The external tooth 22 engaged with the internal tooth 52a of sleeve 52 is provided with input gear 21, in the primary pulley of gear 3 The rotary shaft 33 of 30P fixed pulley 31 is provided with the external tooth 38 that can be engaged with the internal tooth 52a of sleeve 52.
Sleeve 52 is with the CVT positions (C) of neutral position (N), setting via the power transfer path of gear 3, setting warp By each gear of the direct-connected position (D) of the power transfer path of direct-connected gear mechanism 20, by selector fork 53 between each gear quilt Slide driving.
If driving selector fork 53 by electric actuator 50A, sleeve 52 is set to be moved to rotary shaft 33 side, then sleeve 52 Internal tooth 52a engages with the external tooth 38 of rotary shaft 33, and input shaft 2A and primary pulley 30P fixed pulley 31 rotate integrally, setting Via the power transfer path of gear 3.
If driving selector fork 53 by electric actuator 50A, sleeve 52 is set to be moved to the side of input gear 21, then sleeve 52 Internal tooth 52a engaged with the external tooth 22 of input gear 21, input shaft 2A and input gear 21 rotate integrally, and set via direct-connected tooth Take turns the power transfer path of mechanism 20.
Here, in order to also make the external tooth 22 of the internal tooth 52a of sleeve 52 and rotary shaft 33 external tooth 38 or input gear 21 suitable Freely engage, carry out rotation Synchronization Control described later, therefore, lazy-tongs and need not need not be equipped with site of engagement.
In addition, in the present embodiment, as described above, be set to it is unnecessary to perform rotation Synchronization Control and with engaging clutch Mechanism 5A, 5B is together equipped with lazy-tongs, if but be equipped with lazy-tongs, it can obtain and further promote synchronous effect, in addition, Lazy-tongs are must be equipped with the case where being not carried out above-mentioned rotation Synchronization Control.
Reducing gear 6 by being rotated integrally by the rotary shaft 46 with secondary gear 4 in a manner of be fixedly installed gear 61, with Mode with being rotated integrally parallel to the rotary shaft 65 of rotary shaft 46 be fixedly installed and with the meshed gears 62 of gear 61, with rotation Gear 63 that the mode that rotating shaft 65 rotates integrally is fixedly installed, the input gear of differential attachment 7 i.e. with the meshed gears of gear 63 64 are formed.Slowed down between gear 61 and gear 62 according to its gearratio, and then, the basis between gear 63 and gear 64 Its gearratio is slowed down.
(thrust generation mechanism (mechanical counter-force mechanism))
Here, illustrate one of mechanical counter-force mechanism, be provided to secondary pulley 30S thrust generation mechanism 9.As above institute State, the thrust generation mechanism 9 is using torque cam mechanism mechanism.For the torque cam mechanism mechanism (torque cam mechanism device) used herein 90,5~Fig. 9 of reference picture is illustrated.
As shown in figure 5, in the present embodiment, torque cam mechanism mechanism 90 is edge cam, possesses and be fixedly installed on movably The driving cam part (driving cam part) 91 at the back side of belt wheel 35 and driving cam part 91 are abutted and are fixedly installed on Determine in the rotary shaft 36 of belt wheel 34 by driving cam part (inverted cam part) 93, in driving cam part 91 with being driven Between cam part 93 arranged coaxial and the intermediate cam component 92 that can rotate against relative to these cam parts 91,93 this three Individual cam part.Driving cam part 91 is driven by driving cam part 93 in the driving traveling of vehicle (during driving traveling), Driving cam part 91 is driven in vehicle by driving cam part 93 (when being driven to travel) when sliding traveling.So, at this In embodiment, torque cam mechanism mechanism 90 is formed by three cam parts, but is used as the present invention, in torque cam mechanism mechanism 90, Intermediate cam component 92 is not essential, and may be equally applied to the torque cam mechanism mechanism for not possessing intermediate cam component 92.
Driving cam part 91 is the part of cylindric (or ring-type) as shown in Fig. 6 (b) stereogram, and side has at one end There is the first driving cam face 91D of ring-type, another side is fixedly installed on the back side of movable pulley 35.First driving of ring-type is convex All-round two decile of ring-type, respective first driving cam face 91D are had spiral corresponding with defined cam angle degree by wheel face 91D Shape curved surface 91d.Connecting portion 91J is respectively formed with two halved the first driving cam face 91D each other.The connecting portion (first links the joint face that ends of the 91J with the helical form curved surface 91d from side forms and axially extended step-likely Face) 91j, link the second link surface 91k of joint face 91j end and the helical form curved surface 91d of opposite side end.The connection Face 91j shapes on the axis direction (direction parallel with rotation axis) of the rotation axis along driving cam part 91 respectively Into the second link surface 91k is set to the face vertical with axis direction.
By driving cam part 93 be with 91 symmetrical shape of driving cam part, be that the stereogram for making Fig. 6 (b) inverts Shape.The stereogram for continuing to use Fig. 6 (b) illustrates, and side has the first of ring-type by driving cam face 93C, the other end at one end Side is fixedly installed on rotary shaft 36.The first of ring-type is convex by driving by all-round two decile of ring-type, each first by driving cam face 93C Wheel face 93C has helical form curved surface 93c corresponding with defined cam angle degree.In two first be divided by driving cam face 93C's is respectively formed with connecting portion 93J each other.Connecting portion 93J has the end step from the helical form curved surface 93c of side Joint face (the first link surface) 93j, link joint face 93j end and the helical form of opposite side that shape is formed and axially extended Second link surface 93k of curved surface 93c end.Joint face 93j is respectively along by the rotation axis of driving cam part 93 Axis direction (direction parallel with rotation axis) on formed.Joint face 93j is also respectively by the axle of driving cam part 93 Line side is upwardly formed, and the second link surface 93k is set to the face vertical with axis direction.
Intermediate cam component 92 is the part of cylindric (or ring-type) as shown in Fig. 6 (a) stereogram, and side has at one end Have the second of the ring-type relative with the first driving cam face 91D of driving cam part 91 by driving cam face 92D, in the other end Side have with by the first of driving cam part 93 by the second driving cam face 92C of the relative ring-types of driving cam face 93C.In Between cam part 92 relative to driving cam part 91, played a role as by driving cam part, relative to by driving cam Part 93, played a role as driving cam part.The second of ring-type is by the 92D such as Fig. 6 (a) of driving cam face Suo Shi, by ring-type All-round two decile, each there is helical form curved surface 92d corresponding with defined cam angle degree.In two first drivings being divided Cam surface 92D's forms connecting portion 92J respectively each other.Connecting portion 92J has from the helical form curved surface 92d of side end Step-like formation and joint face (the first link surface) 92j, link joint face 92j end and the spiral shell of opposite side axially extended Revolve the second link surface 92k of shape curved surface 92d end.Joint face 92j is also respectively in the axis direction of intermediate cam component 92 Upper formation, the second link surface 92k are set to the face vertical with axis direction.
Second driving cam face 92C of ring-type is to make Fig. 6 (a) by the symmetrical shapes of driving cam face 92D with second The shape of stereogram upset.Second driving cam face 92C also by all-round two decile of ring-type, each has and defined cam angle Helical form curved surface 92c corresponding to degree.Connecting portion is formed by driving cam face 92C respectively each other in two first be divided 92J.Connecting portion 92J has from step-like the first company for being formed and being axially extended in the helical form curved surface 92d of side end Second link surface 92k of junction 92j, the end for linking the first link surface 92j and opposite side helical form curved surface 92d end. First link surface joint face 92j is also formed on the axis direction of intermediate cam component 92 respectively, the second link surface 92k be set to The vertical face of axis direction.
Thus, it is supposed that by the first driving cam face 91D and second by driving cam face 92D each helical form curved surface 91d, 92d is set to the spiral of right-hand thread shape, then first by driving cam face 93C and the second driving cam face 92C each helical form curved surface As the spiral of left-hand thread shape.
In addition, the second of intermediate cam component 92 makes phase to rotation by driving cam face 92D and the second driving cam face 92C Turn direction skew and formed.That is, two second the first link surface 92j by driving cam face 92D and connection two second are connected Driving cam face 92C the first link surface 92j makes phase be offset to direction of rotation and configure and formed.Two cam surface 92D, 92C's Phase offset maximum can be set to 90 degree.Thereby, it is possible to shorten the axial length of intermediate cam component 92.
The second of intermediate cam component 92 can be with the first driving cam face of driving cam part 91 by driving cam face 92D 91D is contacted, the second driving cam face 92C of intermediate cam component 92 can with by the first of driving cam part 93 by driving cam Face 93C is contacted.But between two driving cam face 91D, 92D and two are clamped with ball (steel between driving cam face 93C, 92C Pearl) 95, torque cam mechanism mechanism 90 is configured to ball torque cam mechanism device.
Therefore, as shown in Fig. 6 (a), (b), the first driving cam face 91D, intermediate cam portion in driving cam part 91 The second of part 92 by driving cam face 92D and the second driving cam face 92C, by the first of driving cam part 93 by driving cam On face 93C helical form curved surface etc., be respectively formed with the section arc-shaped for being clamped with ball 95 groove (guide groove) 91g, 92G, 93g.Thus, each driving cam face 91D, 92C between driving cam face 93D, 92C by the point based on ball 95 with respectively being contacted And swimmingly slide.
In addition, in the present embodiment, it is convex by the drivings of driving cam face 92D and second by the second of intermediate cam component 92 Wheel face 92C each groove 92G is configured to store a greater part of guide groove (deep trouth) of ball 95, by the first of driving cam part 91 Driving cam face 91D and it is configured to be accommodated in by driving cam face 93C each groove 91g, 93g by the first of driving cam part 93 The shallow slot (here, section is partial arc shape) that the prominent top of ball 95 in each groove 92G is slipped.
Here, 10~Figure 13 of reference picture illustrates to the composition for loading ball 95 in each groove 92G.
As shown in Figure 10, the groove 92G of intermediate cam component 92 possesses：Be formed as the second quilt along intermediate cam component 92 Driving cam face 92D and the second driving cam face 92C helical form curved surface 92d, 92c spiral helicine helical form groove portion 92g；Shape Into the connection groove section 92m in the mutual of helical form groove portion 92g and smoothly connecting helical form groove portion 92g.Connection groove section 92m Be formed as the part helix shape with helical form groove portion 92g reversed dips in the circumferential, with smooth curved surface and helical form groove portion 92g Between connect.Therefore, groove 92G by these helical form groove portion 92g and connection groove section 92m by throughout complete cycle it is continuous in a manner of formed, The movement of ball 95 is smoothly guided throughout complete cycle.
In groove 92G inside, with the mutual sliding contact of series connection and rotatably equipped with multiple balls 95.Cause This, during as slided traveling, be alternately in driving cam part 91 and by the direction of transfer of the moment of torsion of driving cam part 93 The driving of cam part 91,93 and by driving it is alternate in the case of, the ball 95 inside groove 92G is not influenceed alternately by this.This Outside, lubricating oil is supplied to groove 92G inside, the rotation of each ball 95 of groove 92G inside is extremely swimmingly carried out.
As shown in Figure 11~Figure 13, groove 92G is formed as the section partial circular bigger than semicircle scope, keeps ball 95 and limits The disengaging of ball 95 processed.That is, groove 92G possesses in helical form groove portion 92g as illustrated in fig. 13 makes a part for ball 95 can be from spiral shell The opening portion 98 that shape curved surface 92d is protruded is revolved, stores half portion (lower half in Figure 13) part more than ball 95.
In addition, in two edges of opening portion 98 formed with mutually relative cantilever portion 98a, 98a, cantilever portion 98a, 98a The opening wide cut w of i.e. opening portion 98 is formed as smaller than the outside diameter d of ball 95 each other.Thus, keep ball 95 and limit ball 95 disengaging.In addition, helical form groove portion 92g cross section is formed as the internal diameter part circular more slightly larger than the outside diameter d of ball 95.
But in order to load ball 9 in the groove 92G of the opening portion 98 smaller than the outside diameter d of such ball 95, such as Figure 11 (a), (b) and Figure 13 (b), shown in (c), outside diameter d the earth of the part formed with than ball 95 in opening portion 98 is expanded The insertion in footpath wide diameter portion 96.Thus, can be seated in from insertion wide diameter portion 96 by ball 9 in groove 92G.
In the anti-delinking part that the insertion wide diameter portion 96 departs from formed with the ball 95 after preventing filling from groove 92G inside. The anti-delinking part of present embodiment by by by insertion with wide diameter portion 96 it is expanding it is partially enclosed in a manner of the shape of screwed part 99 installed Into.That is, in the both sides thread mill drilling 97 of insertion wide diameter portion 96, after the ball 95 of whole is loaded, in each screwed hole Couple screwed part 99 in 97.In part of the head of screwed part 99 formed with section Yu cantilever portion 98a similar shapes, coupling After screwed part 99, also turn into the cross sectional shape same with cantilever portion 98a, 98a with the section of wide diameter portion 96 in insertion, prevent Ball 95 after filling departs from from the inside 92G of groove, and is smoothly rolled in groove 92G without prejudice to ball 95.In addition, anti-delinking part Screwed part 99 is not limited to, for example, it is also possible to consider make cam surface 92d (upper in Figure 13 (a) outward in insertion wide diameter portion 96 Side) thicken, after the ball 95 of whole has been loaded, from foreign side by the portion compresses, it is consequently formed and cantilever portion 98a similar shapes Part.
But it is less than half that insertion is formed to the overhang of axial direction with wide diameter portion 96 on helical form curved surface 92d Position.That is, helical form curved surface 92d such as can also will be complete prominent to the overhang of axial direction to axially projecting according to phase angle The position of less than half of output is referred to as helical form curved surface 92d concave side, by a medium-sized position of the overhang than full overhang Referred to as helical form curved surface 92d convex side, insertion wide diameter portion 96 are formed at the concave side (reference picture 10).
Its reason is because of when being formed at helical form curved surface 92d concave side, relative to relative cam part 91,93 Cam surface 91D, 93C, sliding region is elongated, and more balls 95 contact with two cam surface 91D, 92D or 92C, 93C.Therefore, spiral shell The part (recess) of rotation shape curved surface 92d concave side disperses stress, is applied to insertion wide diameter portion 96 and its easy of surrounding is led Cause the stress at the position of stress concentration also to mitigate, durability can be improved.
Figure 14 (a) is the expanded view for the heeling condition for schematically showing groove 92G, and Figure 14 (b) is groove 92G plan. It is assumed that groove 92G helical form groove portion 92g all contributes to the stroke of cam mechanism, if cam path center radius is R (reference pictures 14 (b) when the circulation cam return angle that), the necessary stroke of cam mechanism is the connection groove section 92m shown in L, Figure 14 (a) is θ ', Cam angle degree θ shown in Figure 14 (a) can be represented by the formula.
θ=tan-1(L/ (π R-L/tan θ '))
Here, for example it is assumed that when R=40 (mm), L=20 (mm), θ '=45 (deg),
θ=10.7 (deg).
But as shown in Figure 14 (b), insertion is being set to the rising from helical form groove portion 92g with the position of wide diameter portion 96 When starting point 0 (deg) plays the position for angle ε (deg), ε lower physical limit value εminSuch as following formula (a).
εmin=(L × sin θ × cos θ) × 360/ (2 × π × R) (a)
But consider the deviation etc. of the tool diameter and equipment for cam groove processing, and consideration instrument and cam surface Situation about being vertically processed, such as by lower physical limit value εmin3 times or so of length be set as preventing during cam groove processing Instrument interference use is ε lower limit ε in practical useminrWhen, such as following formula (b).
εminr=(L × sin θ × cos θ × 3) × 360/ (2 × π × R) (b)
In addition, leaned on so that insertion to be located to the half on the inclined-plane (helical form curved surface 92d) than cam with the position of wide diameter portion 96 The mode of the recess of downside sets ε higher limit εmaxWhen, such as following formula (c).In addition, n is CAM peak numbers.
εmax=(2 × π × R/n)-L/tan θ ') × 360/ (4 × π × R) (c)
Therefore, ε (deg) scope such as following formula (d).
εminr＜ ε ＜ εmax···(d)
Here, for example it is assumed that when being R=40 (mm), L=20 (mm), θ '=45 (deg), n=2, ε (deg) scope is such as Following formula (e).
15.70 (deg) ＜ ε ＜ 75.68 (deg) (e)
That is, because insertion with the position of wide diameter portion 96 is in the scope, so when can reliably prevent from declining in lower limit side Instrument interference, can suppress in the upper limit side stress near insert port circumferential component concentrate, it is possible to increase durability.
In addition, by lower physical limit value εmin3 times or so of length be set to lower limit in practical use and (prevent the interference of instrument Lower limit) εminr, but prevent the lower limit ε of the interference of instrumentminrNot limited to this, can be in lower physical limit value εminOn add Ormal weight based on the insert region of instrument and set etc..
Describe the action mechanism of the torque cam mechanism mechanism 90 in detail.
If driving cam part 91 and producing phase offset by driving cam part 93, such as shown in Fig. 7 (a), driving is convex First driving cam face 91D of wheel component 91 and the second of intermediate cam component 92 are engaged by driving cam face 92D, and are driven The first of moving cam part 93 is engaged by driving cam face 93C and the second driving cam face 92C of intermediate cam component 92, driving Cam part 91 and intermediate cam component 92 and by the total axial length of driving cam part 93, i.e. torque cam mechanism mechanism 90 total length most It is small.In this case, the groove width of secondary pulley 30S V-groove is maximum, the gear ratio of gear 3 is most high-grade gear ratio.
In gear 3, when vehicle traction travels, if the input torque transmitted from band 37 to secondary pulley 30S increases By force, then secondary pulley 30S band clamping force deficiency, secondary pulley 30S fixed pulley 34 produce sliding relative to band 37.But It is, because movable pulley 35 relatively-movable with rotary shaft 36 follows band 37, so fixed pulley 34 is relative to movable pulley 35 produce rotatable phase delay.
Now, be fixedly installed on driving cam part 91 in movable pulley 35 via ball 95 driving cam face 91D, Entered line slip between the 92D of driving cam face, meanwhile, as shown in Fig. 7 (b), prior to intermediate cam component 92 and to be fixedly installed on The mode by driving cam part 93 in fixed pulley 34 is rotated against, and with relative to by driving cam part 93 And intermediate cam component 92 axially away from mode move and make movable pulley 35 and fixed pulley 34 close.Its result It is that the groove width of secondary pulley 30S V-groove narrows, belt wheel 30S thrust augmentation, so strengthening with clamping force, eliminates fixation The sliding of belt wheel 34.
On the contrary, when vehicle sliding travels, it is fixed in the state of the negative input torque (braking torque) of driving source effect The rotatable phase delay of belt wheel 34 is eliminated, if relative to negative input torque, secondary pulley 30S band clamping force is insufficient, then (in turn, movable pulley 35 is relative to fixed pulley 34 in advance relative to the generation of movable pulley 35 rotatable phase for fixed pulley 34 Produce rotatable phase delay).
Now, be fixedly installed in fixed pulley 34 by driving cam part 93 via ball 95 by driving cam face Slided between 93C, driving cam face 92C, also, as shown in Fig. 7 (c), with prior to intermediate cam component 92 and be fixedly installed on can The mode of movable cam part 91 on movable belt pulley 35 is rotated against, and with relative to driving cam part 91 and centre Cam part 92 axially away from mode move, make movable pulley 35 and fixed pulley 34 close.As a result, secondary pulley The groove width of 30S V-groove narrows, belt wheel 30S thrust augmentation, and therefore, band clamping force strengthens, and eliminates the cunning of fixed pulley 34 Move.
In addition, when vehicle stops etc., driving torque and braking torque do not work, so will not apply torque cam mechanism The thrust of belt wheel caused by mechanism 90.Then, applied equipped with to movable pulley 35 to the direction for making it close with fixed pulley 34 The helical spring 94 of power, also being capable of anti-stop-band sliding and reliably clamping band 37 with vehicle launch etc. during initial driving.
(gear)
As shown in figure 1, primary pulley 30P gear 8 is provided to by electric actuator 80A and mechanical counter-force mechanism 80B is formed.The situation of present embodiment, mechanical counter-force mechanism 80B use torque cam mechanism mechanism.
The movable pulley 32 of torque cam mechanism mechanism configuration in primary pulley 30P used by mechanical counter-force mechanism 80B Back, there is a pair of cams part 83,84 of the arranged coaxial in rotary shaft 33.Formed respectively on each cam part 83,84 Have makes respectively relative to direction inclined spiral helicine cam surface 83a, the 84a orthogonal with rotary shaft 33, a pair of cams part 83,84 From cam surface 83a, 84a contact and configure.But here, sliding cam surface 83a, 84a mutual installation ball (steel ball) 85, using the ball torque cam mechanism mechanism that sliding part is formed as to the point contact based on ball 85, each cam surface 83a, 84a are swimmingly slided.
Cam part 83 and cam part 84 can be rotated against with rotary shaft 33, primary pulley 30P fixing band Wheel 31 and movable pulley 32 independently coaxially arrange with rotary shaft 33.That is, even if primary pulley 30P rotates, cam part 83,84 Also do not rotate.But cam part 84 be by fixed fixation cam part on direction of rotation and axial direction, on the other hand, Cam part 83 can be rotated against relative to cam part 84 and in axially also moveable movable cam part.In addition, On movable cam part 83, it is provided with side opposite with cam surface 83a and is slided via thrust bearing etc. and the back side 32a of movable pulley 32 The sliding face 83b connect.
Electric actuator 80A is by rotation driving movable cam part 83 and makes the cam surface 83a of movable cam part 83 Rotate relative to the cam surface 84a of fixed cam part 84, make movable cam part 83 along cam surface 83a, cam surface 84a The axle for being tilted in rotary shaft 33 moves up, and movable pulley 32 is moved up in the axle of rotary shaft 33, adjustment primary pulley 30P V-groove groove width.
In addition, electric actuator 80A is by including screw rod (helical gear) 82a and the worm gear (helical teeth engaged with screw rod 82a Wheel) 82b screw gear mechanism 82, drive screw 82a motor 81 form, and worm gear 82b is configured at rotary shaft 33 On coaxial, by rotated integrally with movable cam part 83 and in a manner of allowing movable cam part 83 in the movement of axial direction with it is movable The periphery sawtooth of cam part 83 combines.Thus, act motor 81 and during drive screw 82a, worm gear 82b rotations, Rotate movable cam part 83, the groove width of adjustment primary pulley 30P V-groove.
The groove width adjustment of the V-groove for the primary pulley 30P that the gear 8 is carried out is receiving to be produced by thrust generation mechanism 9 Implement while raw secondary pulley 30S thrust.When by the groove width constriction of primary pulley 30P V-groove so that via The groove width of the secondary pulley 30S of band connection V-groove expands, and with thrust generation mechanism 9 caused by thrust it is relative.By primary When the groove width of belt wheel 30P V-groove expands so that the groove width constriction of secondary pulley 30S V-groove, utilize thrust generation mechanism 9 Caused thrust.
For example, when by the groove width constriction of primary pulley 30P V-groove, motor 81 is acted, makes movable cam part 83 separate from fixed cam part 84.Corresponding, band 37 expands relative to primary pulley 30P winding radius, band 37 Tension force increase.The tension force increase of the band 37 is worked in a manner of band 37 is reduced relative to secondary pulley 30S winding radius. Need to make the groove width of secondary pulley 30S V-groove to expand relative to the diminution of secondary pulley 30S winding radius with 37, secondary In level belt wheel 30S thrust generation mechanism 9, the effect of the groove width that created antagonism as thrust expansion.Therefore, electric actuator 80A resists the thrust and drives movable cam part 83.
In addition, when the groove width of primary pulley 30P V-groove is expanded, motor 81 is acted, makes movable cam part 83 is close with fixed cam part 84.Now, band 37 reduces relative to primary pulley 30P winding radius, and the tension force of band 37 subtracts It is small.Reducing the sliding for producing secondary pulley 30S and band 37 with 37 tension force, secondary pulley 30S movable pulley 35 follows band 37, But fixed pulley 34 produces sliding relative to band 37.It is corresponding with the sliding, produced in fixed pulley 34 and movable pulley 35 Torsion.It is corresponding with the torsion of the fixed pulley 34 and movable pulley 35, secondary pulley 30S thrust augmentation.
(auxiliary motor)
In addition, it is provided with the gear 3 of the automatic transmission 2 and direct-connected auxiliary of primary pulley 30P rotary shaft 33 Help motor 10.The auxiliary motor 10 is for the rotation driving in the switching action carried out by meshing clutch mechanism 5A Rotary shaft 33, promote the rotation of the input side and outlet side of any speed change level of secondary gear 4 synchronous and be equipped with.
(control device)
As shown in figure 1, the vehicle possesses EVECU110 and (the secondary change of band of control automatic transmission of Comprehensive Control electric automobile The CVT of fast mechanism) 2 major part CVTECU100.Each ECU is respectively what is be made up of memory (ROM, RAM) and CPU etc. Computer.Information of the CVTECU100 based on the instruction from EVECU110 or information or from other sensor classes, control structure Motor 81, switching into the electric actuator 80A of gear 8 electric actuator 50A, 50B and auxiliary motor 10 Action etc..
(functions and effects)
Present embodiment is formed as described above, so following functions and effects can be obtained.
Automatic transmission 2 is that secondary gear is added on gear (band type stepless speed changing mechanism pair gear) 3 (always engagement type parallel-axis type gear shift) 4 and direct-connected gear mechanism 20 and form, therefore, CVTECU100 for example can Enough substantially three power transfer modes as shown in Figure 3 are used using the speed change figure shown in Fig. 4, selection.
In common vehicle start, as shown in Fig. 3 (a), select that secondary gear 4 is set into 1 speed using gear 3 The CVT low modes of (low grade).After starting, speed is when rising, and as shown in Fig. 3 (b), selection uses gear 3 by secondary speed change Mechanism 4 is set to the CVT high range modes of 2 fast (top grades).Generally, a variety of transport conditions are coped with the CVT high range modes.
So, by using secondary gear 4, as shown in figure 4, can from by secondary gear 4 be set to 1 speed it is (low Shelves) CVT low modes under make gear 3 be deep low gear state (1st Low), to by secondary gear 4 be set to 2 speed Make to enter in the big variator ratio range that gear 3 is most high-grade state (2nd High) under the CVT high range modes of (top grade) Every trade is sailed, if can expand the gear ratio amplitude of automatic transmission 2, can reduce the burden of the motor 1 of driving source, Neng Goushi The densification for the PWTN entirety that the miniaturization of existing motor 1 is brought, or the efficient area of motor 1 can be used Domain, therefore, it is possible to improve power-train efficiency, by increasing capacitance it is possible to increase the endurance distance of electric automobile.
In addition, vehicle when super expressway etc. is run at high speed, as shown in Fig. 3 (b), uses direct-connected gear mechanism 20. Thus, the power transmission that the high gear band of transmission efficiency comes can be achieved, from this point of view, can also improve consumption efficiency, energy Enough increase the endurance distance of electric automobile.In addition, as shown in phantom in Figure 4, if the gear ratio that direct-connected gear mechanism 20 is realized It is set as more slightly higher than the gear ratio of 2 fast deep low gear, then can mitigates the burden of the motor 1 when running at high speed, it helps increase The endurance distance of electric automobile.
In addition, the switching of three power transfer modes realizes rotation synchronously using motor 1 and auxiliary motor 10, because This can promote rotation synchronous and shorten shifting time, and can also reduce gear shift shock.In addition, pass through motor 1 and auxiliary Help the rotation of motor 10 synchronous, synchronous adjustment can be appropriately carried out, lazy-tongs etc. are omitted, installation cost can be reduced.
For example, when switching secondary gear 4 by meshing clutch mechanism 5B with 1 fast (low grade) and 2 fast (top grades), make The rotation of the rotary shaft 43 of secondary gear 4 is synchronous with the rotation of gear 41 or gear 42, therefore, by making motor 1 and auxiliary The co-operating of motor 10 is helped, the big inertia mass of gear 3 can be overcome, quickly get synchronization, speed change can be shortened Time.
In addition, by meshing clutch mechanism 5A, in the state using gear 3 and direct-connected gear mechanism 20 is used When switching under state, make meshing clutch mechanism 5A input rotary part and output rotary part rotation synchronous, on the other hand, can profit With motor 1 and auxiliary motor 10.
For example, from the case that the state using direct-connected gear mechanism 20 switches to the state using gear 3, can press Following order promptly switches.
(1) meshing clutch mechanism 5A, 5B are set to neutral.
(2) control is carried out as follows by auxiliary motor 10：Promote the rotary shaft of secondary gear 4 via gear 3 43 and with the speed change level of realization corresponding to gear (gear 41 or gear 42) rotation it is synchronous, meanwhile, make driving source i.e. motor 1 Rotation it is synchronous with the rotation of input unit (primary pulley) 30P of gear 3 rotary shaft 33.
(3) the meshing clutch mechanism 5A of neutral position state is switched into CVT positions (C), makes the part (set of input shaft 2A sides Cylinder 52 internal tooth 52a) and gear 3 primary pulley 30P input rotary part (external tooth 38 of rotary shaft 33) engage, and And the meshing clutch mechanism 5B of neutral position state is switched into corresponding with the speed change level to be realized gear (gear 41 or gear 42) link.
Thereby, it is possible to switch meshing clutch mechanism 5A, 5B in a short time, it is not easy to assign moment of torsion and lose to feel, can makes The driving sense related to speed change is good.
In addition, the rotation when auxiliary motor 10 of present embodiment is due to being only used for speed change is synchronous, therefore, can use small The miniature motor of output, it is capable of the cost increase of restraining device.
In addition, vehicle drivetrain unit power transfer path downstream, in order to which moment of torsion amplification more will be to dynamic Power transmission system applies high pulling torque, so, if connected in the primary 30P of the relatively upstream side of power transfer path rotary shaft 33 Auxiliary motor 10, then easily using the miniature motor of small output corresponding with low torque.
In addition, it is also contemplated that the output using the auxiliary motor 10 aids in as the moment of torsion for vehicle traction, the situation Under, auxiliary motor 10 is using the motor exported accordingly.
On the other hand, when switching to the state using direct-connected gear mechanism 20 from the state using gear 3, two are nibbled Close clutch mechanism 5A, 5B and be set to neutral.Moreover, the rotation of control motor 1 makes it synchronous with the rotation of input gear 21.Rotation After turning synchronization, the meshing clutch mechanism 5A of neutral position state is switched into direct-connected position (D), makes the part (set of input shaft 2A sides Cylinder 52 internal tooth 52a) and the side of input gear 21 part (external tooth 52a) engage.
In addition, meshing clutch mechanism 5B keeps neutral in direct-connected driving period.
In addition, according to torque cam mechanism mechanism (torque cam mechanism device) 90, following functions and effects are obtained.
During driving, i.e., from driving cam part 91 to by driving cam part 93 enter action edge transmit when, driving cam portion First driving cam face 91D of part 91 and the second of intermediate cam component 92 are abutted by driving cam face 92D, when sliding, i.e. from During by driving cam part 93 to driving cam 91 passing power of part, by the first of driving cam part 93 by driving cam face 93C and the second driving cam face 92C of intermediate cam component 92 is abutted, and realizes power transmission.
These be ring-type the first driving cam face 91D and second by driving cam face 92D and first by drive it is convex Wheel face 93C and the second driving cam face 92C, can each be formed throughout the all-round of ring-type, it can be ensured that as far as possible to be all-round convex The length of wheel face.
Fig. 9 (a) is schematical side face view when torque cam mechanism device is formed without using intermediate cam, such as Fig. 9 (a) It is shown, driving cam face 192D and can only be ensured by driving cam face 192c each ring-type all-round half cam surface length Degree.On the other hand, Fig. 9 (b) is the difference of height for the cam surface for setting this torque cam mechanism mechanism 90 in the same manner with Fig. 9 (a) composition Schematical side face view when (corresponding with cam stroke)., can be throughout the complete of ring-type in the case of this torque cam mechanism mechanism 90 Form each cam surface 91D, 93C (also having cam surface 92D, 92C (not shown)) week, the length of cam surface can be made generally to double Add.The result is that, it can be ensured that cam stroke amount, meanwhile, although without using intermediate cam, the inclination angle of cam surface can be made It is smaller than tilt angle alpha 1 (the ＜ α 1 of α 2) to spend α 2, generation thrust can be increased.
In addition, each joint face 91j, 92j, 93j are respectively along the direction of the rotation axis (side parallel with rotation axis To) on formed, so torque cam mechanism mechanism 90 promptly acts.
That is, in torque cam mechanism mechanism 90, in driving, as shown in Fig. 8 (a), turn into from driving cam part 91 to quilt The state of the passing power of driving cam part 93, the first driving cam face 91D pressing intermediate cam portions of driving cam part 91 The second of part 92 is by driving cam face 92D (reference arrow F1), the joint face 92j of intermediate cam component 92 and by driving cam portion The joint face 93j of part 93 is abutted.
Joint face 92j, 93j are upwardly formed along the side of rotation axis respectively, so second by driving cam face 92D, along joint face 92j, 93j on rotation axis direction force component F2, thus, such as Fig. 8 (b) institutes of intermediate cam component 92 Show, by by the pressing of the side of driving cam part 93, the second driving cam face 92C of intermediate cam component 92 and by driving cam portion The first of part 93 is abutted by driving cam face 93C.
In addition, during from driving cam part 91 to by driving cam 93 passing power of part, as shown in Fig. 8 (c), driving is convex First driving cam face 91D of wheel component 91 is slided along the second of intermediate cam component 92 by driving cam face 92D, and generation pushes away Power F3.
So, torque cam mechanism mechanism 90 promptly acts.
On the other hand, as shown in Fig. 8 (d), if the end face 91j ' of cam part 91 ', 92 ', 93 ', 92j ', 93j ' not edge Rotation axis inclination, the cam part caused by the pressing force F ' that intermediate cam component 92 receives from driving cam part 91 92 ' and cam part 93 ' collision when moment of torsion, the thrust F4 of its angular metric will be produced, taking makes cam part 92 ' for the time being The movement of the C of cam part 91 ' sides is returned to, therefore the action of torque cam mechanism mechanism 90 can postpone.
In addition, the second of intermediate cam component 92 by driving cam face 92D and the second driving cam face 92C to direction of rotation Phase offset and formed, so the interference on two cam surface 92D, 92C position can be avoided, suppress intermediate cam component 92 Axial length.In the case of present embodiment, two cam surface 92D, 92C phase offset is 90 degree, so at utmost suppress The axial length of intermediate cam component 92.
Moreover, in the case of this torque cam mechanism device 90, intermediate cam component 92 second by driving cam face 92D and On second driving cam face 92C, the guide groove 92G provided with the movement throughout all-round continuously guiding ball 95, so in cam Multiple balls 95 can be installed between face, meanwhile, the angle of inclination for not increasing cam surface ensures that the length of each cam surface.Therefore, Each ball 95 or each cam surface 91D, 92D, 92C, 93C load can be suppressed, for example, in the change for variable v-belt drive In the case of the thrust generation mechanism of fast mechanism, high thrust can be produced not aggrandizement apparatus, and gearratio can be substantially ensured that Scope.
Particularly, guide groove 92G, which possesses, is formed as the spiral helicine helical form groove portion 92g along helical form curved surface 92d, shape Into in the mutual of helical form groove portion 92g and smoothly connecting helical form groove portion 92g connection groove section 92m, so rolling is not limited The movement of pearl 95, resistance to sliding is small, and ball 95 can swimmingly move throughout all-round.
In addition, each cam surface 91D, 92D, 92C, 93C halved helical form curved surface 91d, 92d, 92c, 93c's is mutual Between formed with connecting portion 91J, 92J, 93J.The connecting portion 91J, 92J, 93J possess from two connected each other helical form curved surfaces In side helical form curved surface end to first axially extending link surface 91j, 92j, 93j, link first link surface 91j, 92j, 93j end and second link surface 91k, 92k, 93k of the end of the helical form curved surface of opposite side, second link Face 91k, 92k, 93k are set as the face vertical with axis direction, so driving cam part 91, intermediate cam component can be made by having 92 and by driving cam part 93 axial shortening the advantages of.
In addition, guide groove 92G possesses opening portion 98, a part for ball 95 is protruded outward from opening portion 98, will roll The more than half part of pearl 95 is accommodated, and the opening wide cut of opening portion 98 is formed as smaller than the external diameter of ball 95, so ball 95 not from Guide groove 92G departs from, and is securely held in guide groove 92G.
Guide groove 92G opening portion 98 a part formed with order to ball 95 to be inserted to guide groove 92G inside and Expanding insertion wide diameter portion 96, in insertion wide diameter portion 96, by by insertion with wide diameter portion 96 it is expanding it is partially enclosed in a manner of The screwed part 97 of the anti-delinking part departed from as the ball 95 prevented after inserting from the inside of guide groove is installed, so ball 95 It will not depart from from insertion wide diameter portion 96, be securely held in guide groove 92G.
In addition, insertion wide diameter portion 96 is arranged on above-mentioned angle ε scope, and the half particularly than the inclined-plane of cam is leaned on The recess of downside, in insertion near wide diameter portion 96, usual ball 95 is Multi-contact, so cam part 91,92,93 can Correctly slided along helical form curved surface.For example, as during 1 point of contact, the axle relative to cam part 91,92,93 is produced The inclination in line direction, stress can be suppressed and concentrated to its circumferential component, it is possible to increase durability.
In addition, in the present embodiment, torque cam mechanism mechanism 90 is formed by three cam parts 91,92,93, is used as this hair Bright, in torque cam mechanism mechanism 90, intermediate cam component 92 is not essential, and as shown in figure 15, can also be applied in not possessing Between cam part 92 torque cam mechanism mechanism.
As shown in figure 15, the torque cam mechanism mechanism 90 is by being fixedly installed on the driving cam part at the back side of movable pulley 35 (driving cam part) 91, abutted with driving cam part 91 and be fixedly installed on being driven in the rotary shaft 36 of fixed pulley 34 The two cam parts of moving cam part (inverted cam part) 193 are formed.Driving cam part 91 is when vehicle traction travels Drive by driving cam part 193 (during driving traveling), (gone by driving cam part 193 when vehicle sliding travels by driving When sailing) driving driving cam part 91.
Driving cam part 91 is same with the structure of first embodiment such as shown in Figure 15 (b), so omit the description (ginseng According to Fig. 6 (b)).
It is the shape symmetrical with driving cam part 91, one such as shown in Figure 15 (a) by driving cam part 193 Side has being fixedly installed on by driving cam face 193D, another side in rotary shaft 36 for ring-type.Being driven for ring-type is convex Wheel face 193D is respective to have spiral corresponding with defined cam angle degree by driving cam face 193D by all-round two decile of ring-type Shape curved surface 193d.Halved two are respectively formed with connecting portion 193J each other by driving cam face 193D's.The connecting portion 193J has from the step-like formation in the helical form curved surface 193d of side end and (first links to axially extending joint face Face) 193j, link the second link surface 193k of joint face 193j end and the helical form curved surface 193d of opposite side end.Should Joint face 193j is respectively along by the axis direction (side parallel with rotation axis of the rotation axis of driving cam part 193 To) on formed.Joint face 193j is also formed on by the axis direction of driving cam part 193 respectively, the second link surface 193k is set to the face vertical with axis direction.
Can be with the first driving cam face of driving cam part 91 by driving cam face 193D by driving cam part 193 91D is contacted.Ball (steel ball) 95 is installed between two driving cam face 91D, 193D, torque cam mechanism mechanism 90 is configured to ball torsion Square cam gear.
Therefore, as shown in Figure 15 (a), (b), driving cam face 91D in driving cam part 91, by driving cam part 193 groove by the section arc-shaped on driving cam face 193D helical form curved surface etc., being respectively formed with guiding ball 95 (is led To groove) 91g, 193G.Thus, driving cam face 91D and smooth by being contacted between the 193D of driving cam face by the point of ball 95 Slide on ground.
Moreover, the guide groove 193G by driving cam face 193D by driving cam part 193 of this variation is with implementing The second of the intermediate cam component 92 of mode is same by driving cam face 92D guide groove 92G, possess helical form groove portion 193g and Connection groove section 193m.In addition, guide groove 193G is same with guide groove 92G, possess opening portion (not shown), make one of ball 95 Divide and protruded outward from opening portion, the more than half part of ball 95 is stored, the opening wide cut of opening portion is formed as outer than ball 95 Footpath is small.
In addition, guide groove 193G opening portion a part formed with order to ball 95 is inserted in guide groove 193G Portion and expanding insertion wide diameter portion (not shown), in insertion wide diameter portion equipped with the ball 95 after preventing insertion from guide groove Inside depart from anti-delinking part (for example, screwed part 97).In addition, insertion is arranged on above-mentioned angle ε scope with wide diameter portion, it is special It is not the recess of the half on the inclined-plane than cam on the lower.
By such composition, the same functions and effects of composition corresponding with first embodiment are also can obtain.
In addition, than for keeping the big guide groove of the semicircle of ball 95 to be arranged on the side of driving cam part 91.
(other)
More than, embodiments of the present invention are illustrated, but the invention is not restricted to the embodiment, do not departing from this In the range of invention objective, it can suitably change or partly be implemented using above-mentioned embodiment.
For example, in the first embodiment, in the first driving cam face 91D and intermediate cam portion of driving cam part 91 The second of part 92 is by the 92D of driving cam face, the guiding provided with the ball 95 throughout all-round continuously guiding installation between the two Groove 91g, 93G, wherein, by the second of intermediate cam component 92, by driving cam face 92D guide groove 93G, this side is set to store A greater part of guide groove of ball 95, this side of the first driving cam face 91D guide groove 91g can also be set to store ball 95 a greater part of guide groove and form.
In addition, driven in the second driving cam face 92C of intermediate cam component 92 and by the first of driving cam part 93 On the 93C of moving cam face, guide groove 92G, 93G provided with the ball 95 throughout all-round continuously guiding installation between the two, wherein, Second driving cam face 92D of intermediate cam component 92 guide groove 92G is set to store to a greater part of guide groove of ball 95, But first can also be set to store by driving cam face 93C guide groove 93g this side a greater part of guide groove of ball 95 And form.
In addition, in this second embodiment, in the driving cam face 91D of driving cam part 91 and by driving cam part 93 by the 93C of driving cam face, the guide groove 91g provided with the ball 95 throughout all-round continuously guiding installation between the two, 93G, wherein, by by driving cam part 93, by driving cam face 93C guide groove 93G, this side is set to store ball 95 A greater part of guide groove, but this side of driving cam face 91D guide groove 91g can also be set to store the more than half part of ball 95 Guide groove and form.
But the processing of a greater part of guide groove of storage ball 95 and the processing of special tool(s) is needed, so such as the One embodiment is such, the both ends of intermediate cam component 92 be provided with storage ball 95 a greater part of guide groove, by with Intermediate cam component 92 intensively carries out needing the mode of the processing of special tool(s) to form, and can efficiently be processed.
In addition, in the above-described embodiment, in the composition that meshing clutch mechanism 5A, 5B employ three-position type, make device Form and simplify, the meshing clutch mechanism of two two formulas can also singly be applied in combination in either of which or two sides.
In addition, pulley arrangement 30P, 30S for applying the torque cam mechanism device 90 can be applied not only to above-mentioned electronic vapour Car, and it is also widely applied to hybrid vehicle or engine-driven automobile.
In addition, as mechanical counter-force mechanism, the end cam mechanism shown in embodiment is not limited to, but in edge cam In the case of mechanism, the big mechanism of torque capacity also can be compactly formed.
In addition, in the above-described embodiment, lazy-tongs are not equipped with meshing clutch mechanism 5A, 5B site of engagement, But if being equipped with lazy-tongs in site of engagement, then high accuracy is not required during above-mentioned rotation Synchronization Control, so can revolve Turn to advance with the end of the step and exercise the operation of clutch mechanism 5A, 5B engagement, the time of speed change needs can be shortened.
In addition, in the above-described embodiment, the disengaging of ball 95 is prevented by guide groove 193G, for example, in order to prevent Ball comes off, and with driving cam part, the holding for keeping ball can also be provided separately by driving cam part between cam surface Device.

Claims (5)

1. a kind of torque cam mechanism device of automatic transmission, the rotation torque transmitted in automatic transmission is converted to axial direction by it Thrust, wherein, possess：
Driving cam part, it has the first driving cam face of ring-type, receives rotation torque and rotated；
By driving cam part, its first with the ring-type relative with the first driving cam face is by driving cam face, warp By ball and by the driving cam part rotation driving,
The first driving cam face and described first by driving cam face by all-round at least two deciles, and having respectively of ring-type Helical form curved surface corresponding with cam angle degree, halved helical form curved surface it is mutual formed with connecting portion,
In the first driving cam face and described first by least spiral in the helical form curved surface in driving cam face On shape curved surface, the guide groove for the movement for guiding the ball is continuously provided with throughout complete cycle.
2. the torque cam mechanism device of automatic transmission as claimed in claim 1, wherein,
The connecting portion possesses：
First link surface, it is from the helical form curved surface of the side in the two helical form curved surfaces connected each other by the connecting portion End axially extends；
Second link surface, it links the helical form of the end of first link surface and the opposite side in the two helical forms curved surface The end of curved surface,
Second link surface is set to relative to the vertical face of axis direction.
3. the torque cam mechanism device of automatic transmission as claimed in claim 1 or 2, wherein,
The guide groove possesses：
Helical form groove portion, it is formed as the helical form along the helical form curved surface；
Connection groove section, it forms in the mutual of the helical form groove portion, the helical form groove portion is smoothly connected.
4. such as torque cam mechanism device of automatic transmission according to any one of claims 1 to 3, wherein,
In the inside of the guide groove, multiple balls are equipped with series connection.
5. such as torque cam mechanism device of automatic transmission according to any one of claims 1 to 4, wherein,
Intermediate cam component is also equipped with, it is driven convex formed with can be contacted with the first driving cam face second at one end Wheel face, the other end formed with can with the described first the second driving cam face contacted by driving cam face, relative to the drive Moving cam part and it is described can be rotated against by driving cam part,
From the driving cam part to it is described by driving cam part enter action edge transmit when, the first driving cam face Abutted with described second by driving cam face, action edge biography is being entered to the driving cam part by driving cam part from described When passing, described first is abutted by driving cam face and the second driving cam face, realizes power transmission.
CN201680017852.9A 2015-03-24 2016-02-01 The torque cam mechanism device of automatic transmission Pending CN107429805A (en)

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PCT/JP2016/052856 WO2016152251A1 (en) 2015-03-24 2016-02-01 Automatic-transmission torque cam device

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JP6387180B2 (en) 2018-09-05
US20180080534A1 (en) 2018-03-22

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Application publication date: 20171201